Spring coiling mechanism having a coiling abutment holder operated by a cam operatedyoke



J n- 21, 195 s. EFFRANKS, JR., ETAL 2,820,505

SPRING COILING MECHANISM HAVING A COILING ABUTMENT HOLDER OPERATED BY A CAM OPERATED YOKE Filed Aug. 2, 1955 4 Sheets-Sheet 1 BY 7% 6' MM ATTORNEYS Jan. 21, 1958 E. E. FRANKS, JR. ET AL 2,820

SPRING COILING MECHANISM HAVING A COILING ABUTMENT HOLDER OPERATED BY A CAM OPERATED YOKE 4 Sheets-Sheet 2 Filed Aug. 2, 1955 195 E. E. FRANKS, JR., ETAL 2,820,505

SPRING COILING MECHANISM HAVING A COILING ABUTMENT Jan. 21',

HOLDER OPERATED BY A CAM OPERATED YOKE Filed Aug. 2, 1955 4 Sheets-Sheet 3 47'70//VEY5 E. E. FRANKS, JR.,

Jan. 21, 1958 ET AL' 2,820,505

SPRING COILING MECHANISM HAVING A COILING ABUTMENT HOLDER OPERATED BY A CAM OPERATED YOKE 4 Sheets-Sheet 4 Filed Aug. 2, 1955 ite SPREJG COILING MECHANISM HAVING A COIL- ENG ABUTMENT HOLDER OPERATED BY A CAM OPERATED YOKE Application August 2, 1955, Serial No. 525,896

9 Claims. (Cl. 153-65) The invention relates to a spring coiling mechanism which is preferably a portion of a complete spring coiling machine of the general type disclosed in the Bergevin and Nigro Patent No. 2,119,002 dated May 31, 1938. A mechanism embodying the invention generally resembles that shown in the Halvorsen and Bergevin Patent No. 2,276,579 dated March 17, 1942 and said mechanism is adapted for the making of springs of the type commonly known as torsion springs. Torsion springs are characterized by the provision of uncoiled ends extending at an angle to the spring axis for attachment of the spring as desired, and the present invention contemplates automatic control of the coiling tools of the machine, whereby extended ends of predetermined length may be formed on springs having any desired number of convolutio-ns, without interrupting the feeding of the wire.

One object of the present invention is to provide a mechanism for the stated purpose having improved means for effecting the required movements of the coiling abutment to its inactive and active positions, the last said means being particularly adapted to be readily adjusted for making either right-hand springs or left-hand springs as required.

Another object of the invention is to provide a mechanism having improved means for supporting or holding the coiling abutment and for accurately adjusting the position thereof with respect to the longitudinally fed wire.

Other objects of the invention will be apparent from the drawings and from the following description and claims.

In the drawings we have shown in detail a preferred embodiment of the invention, but it will be understood that various changes may be made from the construction shown, and that the drawings are not to be construed as defining or limiting the scope of the invention, the claims forming a part of this specification being relied upon for that purpose.

Of the drawings:

Fig. 1 is a fragmentary front view of a spring coiling mechanism embodying the invention, the several parts being relatively positioned for coiling right-hand torsion springs.

Fig. 2 is a vertical sectional view taken along the line 22 of Fig. 1.

Fig. 3 is a fragmentary vertical sectional view taken along the line 3--3 of Fig. 1.

Fig. 4 is a fragmentary vertical sectional view taken along the line 4-4 of Fig. 1.

Fig. 5 is a fragmentary vertical sectional view taken along the line 5-5 of Fig. 1.

Fig. 6 is a fragmentary vertical sectional view taken along the line 6-6 of Fig. 1.

Fig. 7 is a fragmentary vertical sectional view taken along the line 7-7 of Fig. 1.

Fig. 8 is a fragmentary vertical sectional view taken along the line 8-8 of Fig. 1.

Fig. 9 is a fragmentary plan view' showing a portion of States atent the coiling abutment and also portions of certain adjacent parts.

Fig. 10 is a schematic view showing the first step in the formation of a spring.

Fig. 11 is a schematic view showing the second step, the several parts being in the relative positions shown in Fig. 1.

Fig. 12 is a schematic view showing the third step.

Fig. 13 is a schematic view showing the fourth step.

Fig. 14 is a schematic view showing the fifth and final step.

Fig. 15 is a view similar to Fig. 1 but showing the several parts in different relative positions for coiling lefthand torsion springs.

Fig. 16 is a fragmentary view similar to a portion of Fig. 1 and showing certain substitute parts which are used for coiling conventional springs.

Fig. 17 is an end view of the arm and coiling abutment as shown in Fig. 16.

Fig. 18 is a fragmentary view similar to the lower por tion of Fig. 1 but showing an alternative construction.

Fig. 19 is a view similar to the lower portion of Fig. 2 but showing the last said alternative construction.

Fig. 20 is a fragmentary partly schematic view illustrating the action of the cams shown in Figs. 18 and 19.

Fig. 21 is a view similar to Fig. 18 but showing-different cams.

Fig. 22 is a view similar to Fig. 19 but showing the same cams as Fig. 21.

A spring coiling mechanism embodying the present invention is or may be a portion of a complete spring coiling machine, such as a machine of the type shown in the Bergevin and Nigro patent before-mentioned. Reference is made to the said patent for a disclosure of the general organization of the machine and of various mechanisms other than the coiling mechanism, such as the diameter control mechanism and the pitch control mechanism.

Referring to the drawings, particularly Figs. 1 to 9 thereof, 10 represents the front portion of the frame of a cyclically operable spring coiling machine of the type shown in said Bergevin and Nigro patent. Supported in part on the frame portion 19 are two longitudinal shafts 12, 12 carrying feed rolls 14, 14. The rolls 14, 14 are, preferably provided with a plurality of pairs of annular grooves for wires of different sizes. There may be three pairs of grooves with the smallest grooves at the front and with the largest grooves at the rear. The shafts 12, 12 are intermittently rotated during each cycle to rotate the feed rolls in the directions indicated, so as to feed a wire 16 to a predetermined extent toward the left and between wire guides 18 and 20. For convenience of description, it will be assumed that the wire 16 is entered in the intermediate sized grooves in said rollers 14, 14. Said feed rolls and the driving means therefor constitute means for longitudinally feeding said wire to a predetermined extent during each cycle and for then interrupting feeding near the end of the cycle.

Also supported in part on the frame portion 10 is a continually rotatable longitudinal cam shaft 22 which Will be assumed to be rotatable in the clockwise direction. While the invention is not necessarily so limited, it will be assumed for present purposes that only one spring is to be made during each rotation of the cam shaft. When only one spring is to be made during each shaft rotation, there is one rotation of the shaft during each cycle. As before stated, the feeding means operates once during each cycle, the intermittent rotation of the feed rolls 14, 14 being in timed relation to the continual rotation of the cam shaft.

A machine embodying the invention may be used for coiling right-hand tension or compression springs having either uniform diameter or variable diameter, or similar left-hand springs, or right-hand torsion springs or lefthand torsion springs. adaptation for any selected type of spring being effected by transposing certain parts and by substituting certain parts. The machine will first be described as set-up and arranged for coiling right-hand torsion springs.

While the general organization of the machine, as shown, is of the type shown in s id Patent 2.119.002. the coiling mechanism. as shown, for torsion springs more closely resembles that shown in the before-mentioned Halvorsen and Bergevin patent.

During each operation of the feed rolls 14. 14 and during each feeding of the wire. said wire is guided by said wire guides 18 and 20 and passes underor over an arbor 24 to produce either a ri ht-hand or a. left-hand spring. The arbor 24 is carried by a slide 25 which is vertically movable in a Q idewav in a tool ho der 26. The arbor 24 'is semicvlindrical and f r a ri ht-hand torsion spring it has a n rmal p ition bel w the l ne of wire feed as shown in Fist. 1. The arb r has a flat face that is ad ted to en a e the vertic l left face .of a wire guide block 27 secured to the said to l h lder 26. For a. ri ht-h nd s rin the block 27 is above the line of wire fe d. The slide 25 and the arbor 2 are biased downwardlv by a spring 28. and during coiling the arbor is held with its upper edge in position to contact the bottom of the wire 16.

Coiling is effected by en ement f the advancing wire with a coiling abutment 30 l cated with its ri ht end adiacent the arbor 24. The end face of he coiling o int mav have a transverse. ordinarilv vertical. ro e 31 for receiv ng the ire. said ro ve bein shown in Fig. 9. As the wire is fed toward the eft it is bent do nward y by the abutment 30 and is c i ed ar und the arbor 24, the coiled s ring movin t ward the front. or awav from the frame plate 10. as coiling proceeds. The coiling operatron is schem ti ally sh wn in Fig. 12 and will be hereina ter more fullv explained.

Carried bv the tool holder 26 is a pitch tool 32 which is su ported bv a stem 33 longitudinally movable in an aperture in said holder. The pitch tool 32 is located below the guide block 27 and it en ages the wire convolutrons during coiling to determine the pitch of the spring. For a uniform spring pitch, the pitch tool 32 can be set 1n a fixed position and for a variable spring pitch it can be moved during coiling by a cam (not shown) on the cam shaft 22. The mechanism for moving the pitch tool 32 or may be as set forth in the said Patents Nos. 2,119,002 and 2,276,579.

I For holding and moving the coiling abutment 30, there is provided a slide 34 guided for horizontal movement along the front of the frame plate It). Carried by the slide 34 at the front thereof is an approximately horizontal arm 36 which is pivotally movable relatively to said slide about a horizontal longitudinal axis extending transversely of the slide and provided by a bolt 38. As shown in Fig. 2, said bolt 38 extends through an aperture in the slide 34 and there is a bushing 40 on the bolt. The bushing 40 fits an aperture in the arm 36, the arm being thus movable about the axis of the bolt.

The arm 36 has a groove extending lengthwise thereof and open at the front, and a holder 42 is located in said groove. The holder is preferably pivoted to the slide for pivotal movement about a transverse pivotal axis substantially parallel to said groove 31 in the coiling abutment and spaced from said abutment in the direction of wire feeding. As best shown in Fig. 3, said axis is ordinarily vertical and is provided by a vertical pivot pin 44 which extends through apertures in the arm and in a boss 45 on the holder 42. The arm 36 has a recess 46 for receiving the said boss 45. A set screw 47 connects the holder 42 with the pin 44. The holder 42 has a groove extending lengthwise thereof and open at the front,

and said coiling abutment 30 is located in said groove, being detachably held by a screw 48.

The holder 42 is movable to a limited extend about the axis of the pin 44 for the adjustment of the coiling abutment 30 forwardly or rearwardly. A screw 50, best shown in Fig. 4, is adapted for moving the holder rearwardly and a screw 52, best shown in Fig. 5, is adapted for moving the holder forwardly. By adjusting said screws the holder 42 and the coiling abutment 30 can be adjusted rearwardly or forwardly to any position within a limited range and can be locked in the adjusted position. By means of this adjustment the above-mentioned vertical groove 31 in the end face of the coiling abutment can be brought into accurate register with the longitudinally fed wire 16.

Secured to the slide 34 is a bracket 54 as best shown in Fig. 6. This bracket has forwardly extending ears which carry vertical stop screws 55, 55. These screws have no function in connection with the coiling of torsion springs and their purpose will be later described.

The coiling abutment 30 is movable toward and from the arbor 24 for determining the diameter of the spring to be coiled. For a spring of unfiorm diameter the abutment is held in a fixed position. When the spring diameter is to be variable, the slide 34 and the parts carried thereby are moved during coiling. For this latter purpose there is provided a bell crank which is at the rear of the frame plate 10 and is movable about the axis of a horizontal longitudinal stud 56. The bell crank has an arm 57 which is connected with the slide 34 by a link 58 in a slot 59 in the frame member 10. The link is connected with the slide by means of a bushing 60 on the said bolt 38. The bell crank has an arm 61 in engagement with a generally vertical link 62 which serves to move the bell crank and the slide 32. The bell crank has a third arm 64 connected with a spring 66 which biases the bell crank for counterclockwise movement and which thus biases the slide 34 for movement toward the left.

A screw 68 having a knob 70 limits movement of the slide towardthe left and the spring 66 tends to hold the slide in engagement with the screw. When the link 62 is inactive the slide 34 may be adjusted by the screw 68 to set the coiling abutment for a spring of any desired diameter within the capacity of the machine. A lock nut 72 serves to lock the screw 68 in any desired position.

A diameter cam, not shown, on the cam shaft 22 and parts associated with said cam serve to move the link 62 vertically and to thus move the bell crank and the slide and the coiling abutment. The spring 66 cooperates with the link 62 for moving said parts in one direction. With the screw 68 backed away, the said diameter cam serves to move or cause the movement of the coiling abutment during coiling so as to vary the spring diameter in the conventional manner as more fully explained in said Patent No. 2,119,002.

The arm 36 and the parts carried thereby including the coiling abutment 30 are cyclically movable about the axis of the pivot bolt 38, said abutment being thus moved to one or the other of its said two transversely spaced positions. For this purpose there is provided a mechanism which includes a cam means or cam 74 on the cam shaft 22 at the front end thereof, said cam preferably comprising two cam plates 74 and 74 rotatively adjustable on said cam shaft. The cam plates have similar rises with faces concentric with the axis and have similar faces having a smaller radius and also concentric with the axis. By relative adjustment the rises on the two cam plates are combined to produce an effective rise of any length within a limited range. As best shown in Fig. 2, the cam plates are carried by a hub 76 secured to the shaft 22 by a set screw 78. An end plate 80 is connected with the hub by screws 82, 82. As shown, a spacing collar 84 is interposed between the end plate 80 and the cam plate 74 and this collar serves to clamp the two cam plates in adjusted positions when the screws 82, 82

are tightened. The collar 84 can be replaced by additional cams for engaging the rollers to impart additional movements to the coiling abutment during the cycle. It will be observed that the rollers have sufficient length to engage with such additional cams.

A reciprocable member is provided adjacent the cam shaft 22 and this member carries at least one and preferably two rollers that are engageable with the cam means or cam 74 on said shaft. As shown, said reciprocable member is a yoke 86 which is pivoted for oscillatory movement about an axis parallel to the cam shaft axis and at one side thereof. Said yoke is movable to a limited extent about a horizontal pivot stud $8 which pro vides said axis and extends forwardly from the frame plate and through a bearing aperture in said yoke. The yoke 86 preferably embraces the cam shaft 22 and is provided with a large central opening through which said cam shaft extends. The yoke preferably engages a suitable stationary guide means at a position remote from said yoke axis, and as shown the guide means comprises two vertical guide strips 96) and 92 connected with the frame plate 10 by screws 94, 94 and 96, 96. The stationary guide means serves to guide said yoke for movement in planes perpendicular to said axis. An alternative guide means for the yoke is shown in Figs. 18 and 21.

Carried by the member or yoke 86 near the bottom thereof is a roller 98 which is rotatable about a longitudinal axis and is engageable with the cam 74. As best shown in Fig. 2, the roller 98 is rotatable on a pin 100, the inner end of which is in an aperture in the yoke and the outer end of which is in an aperture in a block 102. The block 192 is connected to the yoke 86 by screws 104, 104 a shown in Fig. l. The axis of the roller 98 is closely adjacent a vertical plane through the axis of the cam shaft.

Preferably a roller 1%, similar to the roller 98, is carried by the member or yoke 86 near the top thereof and is also engageable with the cam 74-. The two rollers 98 and 106 are equally spaced from the axis of pivotal movement of said yoke as. The roller 196 is rotatable on a pin 108, the inner end of which is in an aperture in the yoke and the outer end of which is in an aperture in a block 119. The block 110 is connected to the yoke by screws 112, 112. The axis of the roller 106 is also closely adjacent said vertical plane through the axis of the cam shaft. Said rollers 98 and 1% are sometimes hereinafter referred to as the first and second rollers.

When the parts are arranged as shown in Figs. 1 and 2, there is provided a spring means which engages the member or yoke to bias it upwardly. Said spring means is preferably a tension spring 114 which engages a pin 116 on the yoke 86 and a pin 118 on the frame plate 10 above the pin 116. The spring 114 is at that side of the shaft 22 which is opposite the pivotal axis of the yoke at 88, and said spring biases the yoke for upward movement about its said axis. As the result of said bias of the yoke, the lower roiler d8 is biased upwardly toward the axis of the cam shaft and into engagement with the cam 74. When the yoke and the lower roller 98 are thus biased upwardly, the upper roller 1% is held away from the cam and does not function.

The yoke 86 is connected with the arm 36 by means of a link 1243 which is pivotally connected at its respective ends with said yoke and arm. Said link is connected with the yoke at an axis which is closely adjacent said vertical plane through the axis of the cam shaft. Preferably and as shown, the link 121) comprises oppositely threaded upper and lower yokes 122 and 124 connected by a turnbuckle 126. The lower yoke 122 is connected with the block 110 by a pivot pin 128, and the upper yoke 124 extends into a recess in the arm 36 and is connected with said arm by a pivot pin 130.

As the cam shaft 22 and the cam 74 are rotated, the roller 98 and the spring 114 cooperates to oscillate the yoke 86. The rise on the cam engages the roller 98 to move the yoke downwardly and the spring 114 moves the yoke upwardly when the rise on the cam passes beyond the said roller. The length of the link is such that the arm 36 and the holder 4-4 hold the coiling abutment 30 in an active position for bending or coiling which position is in alignment with the wire when the yoke is in its lower position and is such that the said arm 36 and holder move the coiling abutment upwardly to an inactive position out of said alignment when the yoke is moved to its upper position.

The arm 36 in its lower or active position is preferably inclined downwardly toward the right so that the center of the coiling abutment 3b is slightly below the wire line. Said lower or active position of the arm and of the coiling abutment can be accurately adjusted by turning the turnbuckle 126 relatively to the yokes 122 and 124. Look nuts are provided for locking the turnbuckle in adjusted position.

In a machine of the type shown in said Patent No. 2,119,002 two cutter shaft heads such as 132 and 134 are provided which are movable about longitudinal axis located below and above the line of wire feed. These heads are oscillated in opposite directions, and they are primarily intended, in the winding of tension or compression springs, for holding cutting tools for cutting ofi completed springs.

When the machine is to be used for coiling torsion springs, the usual cutting tools are omitted and one or the other of the said cutter shaft heads is utilized for carrying an actuating arm 136 which abuts against the arbor slide 25 and which at the proper time moves said slide and the arbor 24 upwardly in opposition to the spring 28. Upward movement of the arbor enables it to cooperate with the wire guide 27 for cutting off the wire as hereinafter more fully explained.

It has been assumed that the wire 16 is in the intermediate grooves in the feed rollers 14, 14. When the wire is so located, the guide blocks 18 and 29 have grooves which register with said intermediate grooves in the rollers, said grooves 138 being shown in Fig. 7. Said blocks 18 and 20 have their front faces spaced only slightly forwardly from said grooves 138. When the wire is in the smaller front grooves in the rollers, other and thicker blocks 13 and 20 (not shown) are substituted which thicker blocks have grooves registering with said smaller front grooves in the rollers. When the wire is in the larger rear grooves in the rollers, other and thinner blocks 13 and 20 (not shown) are substituted which thinner blocks have grooves registering with said larger rear grooves in the rollers.

The guide block 27 has a wire groove 14G corresponding to the wire groove 138 in the upper guide block 18. When blocks 18 and Zti of one thickness are substituted for blocks 13 and 2th of another thickness, the tool holder 26 is adjusted so that the groove 140 in the block 27 aligns with the groove 138 in the block 18. The pitch tool 32 serves not only to control the pitch of the spring but also to hold the wire 16 in said groove 140 in the guide block 27, as best shown in Fig. 8. In any event, the coiling abutment 30 is pivotally adjusted by the screws 58 and 52 so that the groove in said coiling point properly registers with the longitudinally fed wire.

The manner of operation for coiling a right-hand torsion spring will be better understood by reference to the schematic views shown in Figs. 10 to 14.

With the rise of the cam 74 in a position slightly counterclockwise from that shown in Fig. l, the roller 98 will be held by the spring 114 in its upper position and the coiling abutment will be in its upper or inactive position as shown in Fig. It). With the abutment in this position rotation of the feed rollers is started and a length of straight wire 142 is fed above the arbor 24 and below the coiling abutment 30.

The timing is such that after a predetermined wire length 142 has been fed, the continued rotation of the.

cam 74 moves the roller 98 and the yoke 86 to their lower positions as shown in Fig. 1 and the coiling abutment 30 is thus moved from its upper inactive position to its lower active position. In moving to its said lower active position the abutment 30 bends the wire length 142 downwardly around the arbor 24 as shown in Figs. 1 and 11. The wire length 142 constitutes a pro ecting end of the spring that is to be formed. In order not to obscure certain parts of the mechanism, only a portion of the wire length 142 is shown in Fig. 1.

The downward movement of the coiling abutment 30 occurs very rapidly due to the steep rise of the cam 74 so that the continually moving wire, as fed by the rolls, has already started to coil around the arbor 24 by the time the straight end 142 has been bent downwardly. The coiling of the wire around thearbor 24 results in a coil 144, the coil projecting forwardly as it is formed as shown in Fig. 12. Inasmuch as the front faces of the guide blocks 27, 18 and 26 are very close to the wire, said blocks do not interfere with the rotative movement of the wire length or spring end 142 during the formation of the first convolution'of the coil 144. Said coil may be of uniform diameter as shown or it may be given a varying diameter by means of the diameter mechanism described. The pitch of said coil may be varied by movement of the pitch tool 32 by means of the pitch mechanism.

After the wire has been coiled to form a coil 144 of predetermined length, the rise of the cam 74 passes beyond the roller 98 and the spring 114 moves the roller 98 and the yoke 36 to their upper positions and the coiling point is returned to its upper inactive position as shown in Fig. 13. Feeding of the wire continues but the abutment 30 is out of coiling position. The result is that the continued wire feeding moves the coil 144 toward the left, the spring being provided with a straight length of Wire 1146 or spring end opposite the spring end 142.

The feeding of the predetermined wire length 146 is at the end of the cycle and wire feeding is then stopped. Immediately after the interruption of feeding, the cutter shaft 132 is turned to enable the arm 136 to force the slide and the arbor 24 upwardly in opposition to the spring 28. As the arbor 24 moves upwardly, it cooperates with the guide block 27 to cut the wire and thus sever the completed spring as shown in Fig. 14. Wire feeding is thereafter resumed and the described cycle of operations is repeated.

The feed mechanism can be adjusted by mechanism not herein shown, but shown in said Patent 2,119,002, so as to vary the total length of the wire available for each spring. By adjusting the position of the cam 74 and the effective length thereof, the lengths of the projecting spring ends 142 and 146 can be varied and the length of the coil 144 can be varied. It will be obvious that the length of the coil 144 determines the angular relationship between the spring ends 142 and 146. As shown, said ends are at an angle of about 90, but this is not essential.

When the machine is to be used for coiling a left-hand torsion spring, the parts are arranged as shown in Fig. 15, which is similar to Fig. 1 except for the different arrangement. The position of the spring means or spring 114 has been changed so that it engages the said pin 116 on the yoke and a pin 148 on the frame plate below the pin 116. The spring 114 thus biases the yoke 86 downwardly to hold the roller 106 in engagement with the cam. The lower roller 98 is held away from the cam and does not function. The link 1211 moves the arm 36 and the coiling abutment exactly as before with the coiling abutment moving to inactive and active positions, with the exception however that the said parts are moved downwardly instead of upwardly, the coiling abutment being moved to a lower inactive position instead 8 of an upper inactive position as shown in Figs. 9 and 13. The upper and lower inactive positions are sometimes hereinafter referred to as the first and second inactive positions.

A substitute arbor 24 and arbor slide 25 are provided in lieu of the arbor and slide 24 and 25 and the spring 28 is shifted to bias the said parts upwardly instead of downwardly. The actuating arm 136 is shifted to the upper cutter shaft head 134 so that it can move the arbor slide and arbor downwardly instead of upwardly. A guide block 27 located below the wire is substituted for the guide block 27, and a pitch tool 32 above the block 27 is substituted for the pitch tool 32.

Except for reversals of movement, the manner of operation is substantially as described in connection with Figs. 10 to 14, and repetition of the description is unnecessary.

When the machine is to be used for coiling tension or compression springs, whether left-hand or right-hand, the link 1212 is preferably disconnected so that the mechanism is inactive. The link may be disconnected by removing the pin 1313. An alternative holder 150, as shown in Fig. 16, is substituted for the holder 42. The holder 15% is similar to the holder 42 and is similarly mounted, and said. holders 42 and 150 are hereinafter referred to respectively as first and second holders. Each holder when in place extends between the screws 55, 55 on the bracket 54, but the first holder 42 has its right portion relatively thin vertically so as to avoid engagement with said screws and so that the arm 36 and holder are readily movable vertically. The second holder .151 has its right portion relatively thick vertically so as to adapted to be engaged and held by said screws 55,,

The screws maintain the second holder 150 and also the arm 36 in any desired position of vertical adjustment about the axis of the bolt 38.

As shown, the holder 150 carries a coiling abutment 152 which is clamped in. place by a front plate 154 held by screw 156 as shown in Fig. 17. The abutment 152 has a groove 158 therein similar to the groove 31 in the abutment 30. The holder 150 and the coiling abutment 152 can be adjusted about the vertical axis of the pin 44 by means of the screws 50 and 52, the screws 55, 55 being loosened to permit such adjustment. Such adjustment makes it possible for the groove 158 in the coiling abutment to be accurately registered with the longitudinally fed wire.

Furthermore, the screws 55, 55 make it possible for the coiling abutment to be vertically adjusted about the horizontal pivotal axis of the bolt 38. Thus, by means of the screws 59 and 52 and the screws 55, 55, the coiling abutment is universally adjustable.

For conventional coiling the arbor 24 and the slide 25 and the pitch tool 32 are replaced by standard parts such as shown in the said Patent No. 2,119,002, and the machine operates substantially as described in the last said patent. No detailed explanation of operation is necessary.

Figs. 18, 19 and 20 show an alternative construction adapted for the coiling of torsion springs, Figs. 18 and 19 being similar respectively to certain portions of Figs. 1 and 2.

A generally vertically reciprocable yoke 160 is provided which may be generally similar to the yoke 86 and which is so shown. However, as concerns certain of its aspects, the invention is not necessarily limited to a yoke that is pivotally reciprocable. When said yoke is pivotally reciprocable, it is or may be mounted on a pivot stud 162 corresponding to the stud 88. The stud is shown as having a head 163 which cooperates with a washer 164 and other parts to prevent forward movement of the yoke. The yoke 160 is shown as having an arcuate slot 165 which receives a stud on the frame 10 having a head 166 engaging a washer 167 at the front face of the yoke. The last said head 166 and said head 164 on the stud 162 act through said washers to prevent forward movement of the yoke and when said heads and washers are provided the guide strips 90, 92 shown in Figs. 1 and may be omitted.

As shown in Fig. 19, a cam shaft 168 is provided which is similar to the cam shaft 22 but which is somewhat longer. A hub 170 is provided which is similar to the hub '76 but which is somewhat longer. The hub 170 has a flange 171 at its inner end, said flange having a diameter greater than that of the main body of the hub. The lower roller 98 is the same as the lower roller previously described, but it is located at a position substantially forward from the position shown in Figs. 1 and 15. As shown, there is no separate block such as 102 for carrying the roller 98, and said roller is carried by an integral extension 172 on said yoke 160. The upper roller 106 and its directly associated parts are the same as previously described. However, the vertical spacing between the rollers 98 and 106 is somewhat less so that the upper roller is in position to engage the periphery of the hub 170 when the lower roller and the yoke are in their lowermost positions. When the yoke is in its said lowermost position the center line thereof and the pin 116 are slightly below a horizontal line through the pivotal axis of the stud 162.

With a longer hub such as 170 and with the rollers 98 and 106 longitudinally spaced and out of register with each other, there is provision for a wider variety of camming arrangements. As shown in Figs. 18 and 19, a cam 174 is provided having cam plates 174 and 174 and this cam is located adjacent the end plate 80. The plates of said cam are generally similar to the cam plates 74 and '74 but they are shown as having substantially longer rises. The forward location of the cam plates 174 and 174 prevents the longer rises on said plates from interfering with the upper roller 106 as will be clearly evident from Fig. 19.

A cam 176 may be provided for engaging the upper roller 106, said cam having cam plates 176 and 176*. A spacing collar 177 is interposed between the cam 176 and the plate 174* of the cam 174, said collar having the same outer diameter as the flange 171. The major portion of the periphery of the cam 176 has the same radius as the flange 171 and the collar 177, but said cam plate 176 has a rise which is located to engage the roller 106 at about the same time that the cam plate 174 disengages the roller 98. This will be evident from the partly schematic Fig. which shows the cams in their last said positions. The cam 176 will engage the roller 106 during each rotation to positively move the yoke 160 upwardly. This assures more rapid and more certain upward movements than could be expected by the :spring 1114 alone. As shown, the rise 178 on the cam 17.6 serves merely to move the roller 106 and the yoke upwardly, the spring 114 being depended upon to hold them in their upper positions. However, by somewhat increasing the length of the rise 178 on the cam, said cam could hold the roller and the yoke in their upper positions. Thus the upward and downward movements of the yoke 160 and of the parts connected therewith could be effected solely by the cams 174 and 176 and the spring 114 could be entirely omitted.

The arrangement shown in Figs. 18, 19 and 20 is for right-hand springs, but the parts may be rearranged for left-hand springs in the manner previously described in connection with Fig. 15. For left-hand springs the locations of the cams 174 and 176 are reversed, and the location of the spring 114 is also reversed.

Figs. 21 and 22 show the same construction as Figs. 18, 19 and 20 except for different cams. As shown, the cams are formed and arranged for effecting. two movements. of the yoke 160 during each cycle. A cam 180 is provided near the front for engaging the roller 98,, said cam comprising three cam plates 180 180* and 180. The rises of the cam plates 180 and 180 overlap, but a space is provided between them and the rise of the cam plate Thus the roller 98 and the yoke are moved downwardly twice during each cycle, the spring 116 being depnded upon for upward movement. Obviously, cams like the cam 176 may be provided in lieu of the spring, if preferred, for effecting upward movements.

With the carnming arrangement described, the coiling abutment 30 will obviously have two movements during each cycle out of its active or coiling position. The sequence of operations will be as described in connection with Figs. 11 to 14 except that the coiling operation as shown in Fig. 12 will be momentarily interrupted so that the coil 144 will be in two sections or portions with a length of straight wire between the portions.

The camming arrangement shown in Figs. 21 and 22. is merely illustrative and many alternate arrangements will be obvious to those skilled in the art.

The invention claimed is:

1. In a cyclically operable spring coiling machine, the combination of means for longitudinally feeding wire to a predetermined extent during each cycle and for then interrupting feeding near the end of the cycle, a coiling arbor having a normal position adjacent the path of wire feeding, a coiling abutment having an inactive position vertically spaced from said path of wire feeding and having an active position in said path which last said position enables said abutment to serve for coiling the longitudinally fed wire around said arbor, a cam shaft rotatable about a fixed axis and making one rotation during each cycle, a yoke pivoted for oscillatory movement about an axis parallel to the cam shaft axis and at one side thereof, a roller on said yoke having.

its axis closely adjacent a vertical plane through the axis of said cam shaft, a link having a pivotal connection with said yoke at a position closely adjacent said vertical plane and having a pivotal connection with said coiling abutment to enable said yoke to move said abutment upwardly and downwardly, a spring for biasing said yoke in the direction to move said roller toward said shaft axis and to move said link and said abutment in the same direction, a cam carried by said shaft and engaging said roller for cooperation with said spring to oscillate said yoke and thereby move said coiling abutment to and from its active position, said cam being so shaped and so related to said wire feeding means that the coiling abutment is held in its said inactive position during the first portion of each cycle to form a first straight spring end and is held in its said active coiling position during the next following portion of each cycle to form a coil spring and is again held in its said inactive position during the final portion of each cycle to form a second straight spring end, and means operable at the end of each cycle and while feeding is interrupted for cutting said wire at the last said end thereof.

2. A spring coiling machine as set forth in claim 1., wherein the yoke has an opening therein through. which the cam shaft extends, and wherein said spring means is connected with the yoke at that side of the shaft which is opposite the pivotal axis of said yoke.

3. A spring coiling machine as set forth in claim 2, wherein a stationary means is provided at a position at the. side of said cam shaft that is opposite said yoke axis for guiding said yoke for movement in planes perpendicular to said axis.

4-. In a cylically operable spring coiling machine, the combination of a means for longitudinally feeding wire to a predetermined extent during each cycle and for then interrupting feeding near the end of the cycle, a coiling arbor having alternative first and. second normal positions respectively below and above the path of wire feeding, a coiling abutment having alternative first and second inactive positions respectively above and below said path of wire feeding and having. an active positio yoke respectively below and above said shaft and having L their axes closely adjacent a vertical plane through the axis of said cam shaft, a link having a pivotal connection with said yoke at a position closely adjacent said vertical plane and having a pivotal connection with said coiling abutment to enable fsaid yoke to move said abutment upwardly and downwardly, spring means having alterna tive first and second positions and serving according to its position for biasing said yoke upwardly so as to upwardly move said first roller and said link and said abutment or for biasing said yoke downwardly so as to downwardly move said second roller and said link and said abutment, a cam carried by said shaft and engageable with either of said rollers according to the position of the spring means so that the engaged roller and the spring means cooperate to oscillate said yoke and thereby move said coiling abutment to and from its first inactive position or to and from its second inactive position, said cam being so shaped and so related to said wire feeding and wire cutting means that the coiling abutment is held in the inactive position that corresponds to the position of the spring means during the first portion of each cycle to form a first straight spring end and is held in its said active coiling position during the next following portion of each cycle to form a coil spring and is again held in its last said inactive position during the final portion of each cycle to form a second straight spring end, and means operable at the end of each cycle and while feeding is interrupted for cutting said wire at the last said end thereof.

5. A spring coiling machine as set forth in claim 4, wherein the yoke has an opening therein through which the cam shaft extends, and wherein said spring means is a tension coil spring connected with the yoke at that side of the shaft which is opposite the pivotal axis of said yoke, said spring being alternatively connectible to bias said yoke upwardly and downwardly.

6. In a cyclically operable spring coiling machine, the combination of means for longitudinally feeding wire to a predetermined extent durin each cycle and for then interrupting feeding near the end of the cycle, a coiling arbor having a normal position adjacent the line of wire feeding, a coiling abutment having an inactive position out of the path of wire movement and having an active position in said path which last said position enables said abutment to serve for coiling for longitudinally fed wire around said arbor, a cam shaft rotatable about a fixed axis and making one rotation during each cycle, a generally vertically reciprocable yoke embracing the cam shaft, lower and upper rollers on said yoke respectively below and above the cam shaft and having their axes closely adjacent a vertical plane through the axis of said cam shaft, a link having a pivotal connection with said yoke at a position closely adjacent said vertical plane and having a pivotal connection with said coiling abutment to enable said yoke to move said abutment, cam means carried by said shaft and respectively engaging said two rollers for moving the lower roller downwardly and for moving the upper roller upwardly during each cycle so as to reciprocate the yoke and thereby correspondingly move said coiling abutment, said cam means being so shaped and so related to said wire feeding means that the coiling abutment is held in its said inactive position during one portion of each cycle to form a first straight spring portion and is held in its said active coiling position during a later portion of each cycle to form a coil spring and is again held in its said inactive position during a following portion of each cycle to form a second straight spring portion, and means operable at the end of each cycle and while feeding is interrupted for cutting said wire adjacent the last said straight portion thereof.

a 7. In a cyclically operable spring coiling machine, the combination of means for longitudinally feeding wire to a predetermined extent during each cycle and for then interrupting feeding near the end of the cycle, a coiling arbor having a normal position adjacent the line of wire feeding, a coiling abutment having an inactive position out of the path of wire movement and having an active position in said path which last said position enables said abutment to serve for coiling the longitudinally fed Wire around said arbor, a cam shaft rotatable about a fixed axis and making one rotation during each cycle, a generally vertically reciprocable yoke embracing the cam shaft, lower and upper rollers on said yoke longitudinally spaced from each other and located respectively below and above the cam shaft and having their axes closely adjacent a vertical plane through the axis of said cam shaft, a link having a pivotal connection with said yoke at a position closely adjacent said vertical plane and having a pivotal connection with said coiling abutment to enable said yoke to move said abutment, two cams carried by said shaft in longitudinally spaced relationship and respectively engaging said two rollers for moving the lower roller downwardly and for moving the upper roller upwardly during each cycle so as to reciprocate the yoke and thereby correspondingly move said coiling abutment, said cams being so shaped and so related to said wire feeding means that the coiling abutment is held in its said inactive position during one portion of each cycle to form a first straight spring portion and is held in its said active coiling position during a later portion of each cycle to form a coil spring and is again held in its said inactive position during a following portion of each cycle to form a second straight spring portion, and means operable at the end of each cycle and while feeding is interrupted for cutting said wire adjacent the last said straight portion thereof.

8. In a cyclically operable spring coiling machine, the combination of means for longitudinally feeding wire to a predetermined extent during each cycle and for then interrupting feeding near the end of the cycle, a coiling arbor having a normal position adjacent the line of wire feeding, a coiling abutment having an inactive position out of the path of wire movement and having an active position in said path which last said position enables said abutment to serve for coiling the longitudinally fed wire around said arbor, a cam shaft rotatable about a fixed axis and making one rotation during each cycle, a yoke pivoted for oscillatory movement about an axis parallel to the cam shaft, lower and upper rollers on said yoke respectively below and above the cam shaft and having their axes closely adjacent a vertical plane through the axis of said cam shaft, a link having a pivotal connection with said yoke at a position closely adjacent said vertical plane and having a pivotal connection with said coiling abutment to enable said yoke to move said abutment, two cams carried by said shaft and respectively engaging said two rollers for moving the lower roller downwardly and for moving the upper roller upwardly during each cycle so as to oscillate the yoke about its said axis and so as to thereby correspondingly move said coiling abutment, said cams being so shaped and so related to said wire feeding means that the coiling abutment is held in its said inactive position during the first portion of each cycle to form a first straight spring end and is held in its said active coiling position during a following portion of each cycle to form a coil spring and is again held on its said inactive position during the final portion of each cycle to form a second straight spring end, and means operable at the end of each cycle 13 and while feeding is interrupted for cutting said wire at the last said end thereof.

9. In a cyclically operable spring coiling machine, the combination of means for longitudinally feeding wire to a predetermined extent during each cycle and for then interrupting feeding near the end of the cycle, a coiling arbor adjacent the line of wire feeding, a slide horizontally movable toward and from said arbor, adjustable stop screws on the slide adjacent the arbor, an arm extending toward said arbor and connected with the slide at the end remote from the arbor for movement about an axis perpendicular to the direction of slide movement, a first holder for a coiling abutment rigidly connectible with the arm and extending between said stop screws and being relatively thin adjacent said screws to avoid engagement therewith so as to be readily movable vertically, a second holder for a coiling abutment selectively interchangeable with said first holder and rigidly connectible with the arm and being relatively thick adjacent said screws for ready engagement therewith so that it may be held against vertical movement, each of 14 first and second holders being selectively adapted to hold a coiling abutment adjacent the arbor so as to serve for coiling the longitudinally fed wire around said arbor with the resultant formation of a series of spring con volutions, and means for cutting said wire after completion of said spring convolutions.

References Cited in the file of this patent UNITED STATES PATENTS 332,268 Mathiason Dec. 15, 1885 721,567 Kelley Feb. 24, 1903 1,118,411 Granz Nov. 24, 1914 1,480,796 Van Orman Jan. 15, 1924 1,655,279 McGowan Jan. 3, 1928 1,795,767 Ekstedt Mar. 10, 1931 2,119,002 Bergevin May 31, 1938 2,276,579 Halvorsen Mar. 17, 1942 2,423,433 Amidon July 8, 1947 2,614,606 Kirchner Oct. 21, 1952 2,655,973 Hoelsch Oct. 20, 1953 

